CN102927198A - Internal combustion engine with mass balancing and method for operating such an internal combustion engine - Google Patents
Internal combustion engine with mass balancing and method for operating such an internal combustion engine Download PDFInfo
- Publication number
- CN102927198A CN102927198A CN2012102796670A CN201210279667A CN102927198A CN 102927198 A CN102927198 A CN 102927198A CN 2012102796670 A CN2012102796670 A CN 2012102796670A CN 201210279667 A CN201210279667 A CN 201210279667A CN 102927198 A CN102927198 A CN 102927198A
- Authority
- CN
- China
- Prior art keywords
- balancing unit
- combustion engine
- internal
- axle
- quality
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/22—Compensation of inertia forces
- F16F15/26—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system
- F16F15/264—Rotating balancer shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
Embodiments for mass balancing an engine are provided. In one example, an internal combustion engine having at least one cylinder which is associated with a crank drive comprises at least one mechanically driven balancing unit for balancing the mass forces, the balancing unit including at least one balancing weight which serves as an unbalance by initially rotating a first mass about a rotational axis relative to a second mass when the balancing unit is operational, and an interrupter unit to disconnect the at least one balancing unit from the mechanical drive in a switched off state and connect it to the mechanical drive in a switched on state.
Description
The cross reference of related application
The application requires the preference of No. the 102011080602.4th, the German patent application submitted on August 8th, 2011, and its full content is hereby expressly incorporated by reference.
Technical field
The present invention relates to internal-combustion engine.
Background technique
For design and the structure of Motor Vehicle and internal-combustion engine, vibration becomes and becomes more and more important.In addition, also attempt to affect and adjust the noise that is produced by internal-combustion engine.According to the theory of noise design, also combine some relevant therewith measures.Internal-combustion engine sound or vehicle noise have played main, conclusive impact to the purchase decision of client when buying vehicle, and this cognition has also promoted this R﹠D work.For example, sporting driver prefers the sort of vehicle that shows vehicle or motor motion feature with noise
In the scope of noise design, compensation (for example remove or eliminate) vibration, the perhaps Independent Vibration of isolation, filtering characteristic frequency, and if necessary, then the Independent Vibration of characteristic frequency carried out modeling.
The source that can be identified as the noise source on the Motor Vehicle comprises: the noise that hydrodynamic noise, sound (solid-borne sound) radiation of propagating owing to solid produce and because the noise that the sound that solid is propagated produces via engine mounting seat introducing automobile body.
For example, hydrodynamic noise comprises noise, induction noise and the fan noise at exhaust outlet place, and because the noise that the acoustic radiating that solid is propagated produces comprises the displacement noise of real engine noise and vent systems.By impact and sound that engine structure that alternating force is vibrated is propagated via the Radiated Noise of Engine Surfaces solid as airborne sound and generate by this way the engine noise of reality.
Introduce the sound that solid is propagated via the engine mounting seat, the sound of especially solid being propagated is introduced automobile body and is even more important for sense of hearing driving comfort.
Internal-combustion engine and relevant secondary assembly are can vibrate and can affect the system of its vibration behavior.Encouraging maximally related parts with excited by impact and power is crankshaft shell, cylinder block, cylinder head, crank driven mechanism, piston and valve drive.These parts stand inertial force and gas force.Here, crank driven mechanism specifically comprises bent axle, piston, wrist pin and connecting rod, and formation can be vibrated and the system relevant with the method according to this invention.
Bent axle stands rotational oscillation by temporal evolution and via the rotating force that the connecting rod that links to each other with corresponding crankpin is introduced bent axle.These rotational oscillations cause the radiation of the sound of being propagated by solid and the noise that produces and introduce vehicle body and internal-combustion engine and the noise that produces by the sound that solid is propagated.When at free frequency scope underexcitation bent axle, can produce larger rotational oscillation amplitude, even can cause fatigue fracture.This shows that interested vibration is not only relevant with the noise design, but also relevant with the intensity of parts.
The rotational oscillation of bent axle is passed to camshaft in unexpected mode via control conveying means or camshaft drive, and wherein, camshaft itself also represents oscillatory system and can make other system (especially valve drive) vibration.In addition, the vibration of bent axle is introduced into power train, can be passed to the tire of vehicle via this power train.
The rotating force distribution of locating at the crankshaft crank (crankshaft throw) of quartastroke engine is periodic, and wherein, the cycle is twice rotation of bent axle.In order to explain the excitation of rotational oscillation, rotating force distributes and usually is decomposed into its harmonic component by Fourier analysis.In this case, actual rotating force distributes and is comprised of constant rotating force and the rotating force that a plurality of harmonic waves with different rotary power amplitude and frequency or vibration rate change.The oscillation rate n of each harmonic wave
iBe called harmonic order i with the ratio of the rotational speed n of bent axle or motor.
Because as the higher dynamic load on the result's of inertial force and gas force the bent axle, when the configuration internal-combustion engine, the artificer attempts to implement the as far as possible mass balance of wide range (for example, optimised).In this case, term " mass balance " is in conjunction with compensating or reducing inertial force to all measures of externalities.With regard to this degree, the method for balance inertial force (mass force) according to the present invention not only relates to such inertial force but also relates to the moment that is produced by inertial force.
In this case, there is the solution for the adjusting of the quantity of crankshaft crank, cylinder and configuration and ignition order, thereby realizes the best quality balance.
Balance in-line arrangement six cylinder engine by this way.Six cylinders are combined into being used as cylinder pair in the mode of their parallel machine operations.Therefore, the first cylinder and the 6th cylinder, the second cylinder and the 5th cylinder and the 3rd cylinder and the 4th cylinder are in conjunction with to form cylinder pair, and wherein, three right crankpin and crankshaft cranks of cylinder are configured to respectively at 120 ℃ of A of bent axle skew.Parallel mechanical movement refers to that two pistons of two cylinders of parallel mechanical movement locate to be positioned at identical ℃ A (crank angle) at top dead center (TDC) or lower dead center (BDC).When selecting suitable ignition order, inertial force is balanced.
In the situation that the in-line arrangement three cylinder engine can also be come balance one order inertia power and second-order inertia power by selecting suitable crankshaft crank and suitable ignition order, but can not balance by the caused moment of inertial force.
Situation such as above-mentioned in-line arrangement six cylinder engine, can not all realize in each case complete mass balance, the result must take further step, for example, configures weight (counterweight) and/or makes internal-combustion engine be equipped with at least one trunnion shaft at bent axle.
The starting point of these measures is to load bent axle by temporal evolution and by the rotating force that gas force and the inertial force of crank driven mechanism forms.The quality of crank driven mechanism, for example, the respective quality of connecting rod, piston, wrist pin and piston ring can be converted to vibration equivalent mass and rotation equivalent mass.By being configured in weight on the bent axle at the inertial force of balance rotating equivalent mass easily aspect its external effect.
More complicated by the caused rotatory inertia equilibrium of forces of vibration equivalent mass, this inertial force is approximate by consisting of with the one order inertia power of engine speed rotation and the second-order inertia power of rotating with engine at twice engine speed, and wherein, more high-order power can be ignored.
In fact can come by the configuration of rotating in the opposite direction and be provided with two axles (being called trunnion shaft) of corresponding weight the rotating inertia force of complete equilibrium arbitrary order.Here, the axle that is used for balance one order inertia power rotates with engine speed, and rotates with engine at twice engine speed for the axle of balance second-order inertia power.
Even in the situation that the complete equilibrium rotating inertia force, because the inertial force of each cylinder acts in the central plane of cylinder, so produce moment of inertia.These moment of inertia can be come in the situation that again compensate separately by being equipped with ponderable trunnion shaft again.
For example in the situation that the in-line arrangement three cylinder engine, can compensate the moment that is caused by one order inertia power by single trunnion shaft, wherein, single trunnion shaft provides two counterweights that are configured and are used as non-equilibrium (unbalance) with 180 ° skew with the engine speed rotation and at its place, end on the direction opposite with bent axle.
A trunnion shaft is provided or provides if necessary a plurality of trunnion shafves not only to increase spatial requirement and cost, and improved fuel consume.On the other hand, the impost by shaft balancing unit especially and the fuel consume that causes increase as the impost of weight non-equilibrium and that obviously increase the gross weight of driver element.On the other hand, the running shaft of balancing unit and other moving members cause the frictional loss of internal-combustion engine and the increase of this frictional loss significantly.Particularly, because if engine starting and the running balancing unit fact of continuous operation always just, the increase of this frictional loss has coherence.For example, because noise design, balance inertial force constantly here, and do not consider whether the instantaneous working state of internal-combustion engine needs this mass balance fully.
Therefore, in the in-line arrangement three cylinder engine of relatively high engine speed, can omit the balance by the caused moment of one order inertia power, this is because the noise that produces by vibrating only is evaluated to have problems during low rotational speed place and idling, and only has the excitation risk in the free frequency zone in this rotational velocity range.On the other hand, can need not mass balance at relatively high rotational speed place.
Summary of the invention
The present inventor has recognized above problem and provides and utilizes relatively low frictional loss to carry out the method for mass balance.Therefore, internal-combustion engine with at least one cylinder that is associated with crank driven mechanism comprises: be used at least one mechanically operated balancing unit of balance inertial force, balancing unit comprises that rotating first quality for the second quality around running shaft by initial phase when balancing unit turns round is used as nonequilibrium at least one counterweight; And interrupted unit, at least one balancing unit and mechanical actuation device are disconnected and under opening state, at least one balancing unit are connected to mechanical actuation device.
For mass balance, internal-combustion engine according to the present invention uses changeable balancing unit, wherein, when the needs balance, can enable (for example opening) changeable balancing unit, but when not needing balance, (for example disconnecting) this changeable balancing unit of for the loss of reducing friction, stopping using.
Can by according to the invention provides the fact that makes the interrupted unit of balancing unit (for example, mass balance) and mechanical actuation device disconnection in order to stop using, switch at least one balancing unit.For this reason, the force flux between mechanically operated balancing unit and mechanical actuation device has to disconnect by for example clutch, and this clutch is opened in order to disconnect balancing unit.
In the situation that in-line arrangement three cylinder engine, can in low rotational speed place and idling mode, carry out mass balance by this way, for loss and the corresponding fuel oil loss of reducing friction, by disconnecting balancing unit for higher rotational speed cancellation mass balance.In the situation that mechanically operated balancing unit, the trunnion shaft of use is configured in the crankcase below usually or preferably.
When reading the following specifically describes separately or by reference to the accompanying drawings, be more readily understood above advantage of the present invention, other advantages and feature by the following specifically describes.
Should be appreciated that, above general introduction is provided, be introduced in simplified form the conceptual choice that further describes in the specific descriptions.Not key or the essential characteristic for definite desired theme, but limit uniquely scope of the present invention by the claim that the following specifically describes.In addition, desired theme is not limited only to solve the mode of execution of any shortcoming described in the above or any part of the present invention.
Description of drawings
Fig. 1 shows the first embodiment of balancing unit.
Fig. 2 a and Fig. 2 c show the side view of the embodiment's of the balancing unit shown in Figure 1 that is in position of rest counterweight (balancing weight).
Fig. 2 b and Fig. 2 d show the side view of counterweight shown in Fig. 2 a that is in the working position.
Fig. 3 has schematically shown the example vehicle that comprises motor and balancing unit.
Fig. 4 shows the flow chart according to the method that is used for balanced engine of the embodiment of the invention.
Embodiment
Fig. 1 shows the first embodiment of balancing unit 1.Shown in balancing unit 1 comprise axle 2, dispose two counterweights 3 that are spaced apart from each other at this axle.
Axle 2 has the actuation gear 4 that also forms mechanical actuation device 4 at free end.In order to interrupt the force flux between balancing unit 1 and/or counterweight 3 and mechanical actuation device 4, provide interrupted unit 6.In the embodiment shown in fig. 1, clutch 6a is as interrupted unit 6, and wherein, clutch 6a is configured between actuation gear 4 and the counterweight 3.
By opening clutch 6a, the force flux between drives interrupts gear 4 and the counterweight 3 and disconnection balancing unit 1.Under opening state, counterweight 3 is connected to mechanical actuation device 4 by closed clutch 6a, and the result is that counterweight 3 can be around running shaft 5 rotations.
In Fig. 1, show two counterweights 3 that are in position of rest, they also are in position of rest in Fig. 2 a.
Fig. 2 a and Fig. 2 b show the embodiment's of the balancing unit shown in Figure 11 that is in position of rest the side view of counterweight 3.Comprise two part 3a, 3b as nonequilibrium counterweight 3, these two part 3a, 3b realize with the form of the wing and can be relative to each other around the running shaft vertical with figure plane 5 rotations.These two part 3a, 3b are configured on axle 2 Rotate 180 °.Therefore, in position of rest, two part 3a, 3b cancel out each other in their external effect.
By rotating a part 3b in two parts, produce imbalance and formation as nonequilibrium counterweight 3.In the working position, two part 3a, 3b no longer have side-play amount, for this reason, and second portion 3b Rotate 180 °.
Fig. 2 b and Fig. 2 d show the side view of counterweight 3 shown in Fig. 2 a that is in the working position, wherein, and by the initial position that has been shown in dotted line second portion 3b among Fig. 2 b, for example position of rest.
Shown in Fig. 2 d, when second portion 3b rotates, in order to rotate together the 3a of first portion and second portion 3b substantial registration around axle.Therefore, can comprise two quality in the balancing unit shown in Fig. 2 b and Fig. 2 d: the first quality and the second quality that in Fig. 2 b and Fig. 2 d, are shown part 3a and 3b.When not enabling balancing unit, when for example being in position of rest, the first quality and the second quality relative to each other are configured on the opposite side of axle, and for example the second quality can be with respect to the first quality Rotate 180 °.When enabling balancing unit, the second quality can be with respect to the first Mass movement, until the first quality and the second quality are aimed in the same side of axle.
For with respect to the first Mass movement the second quality, the first quality and second quality that can be configured on the axle comprise a plurality of parts that are configured to be rotated independently of one another.Therefore, part of the axle of configuration the first quality can keep static on it, and part of the axle of configuration the second quality can be rotated on it.In case quality is aimed at, the part of axle just can be rotated together.Alternatively, the second quality can be moved into aligning via electromagnetic mechanism, hydraulic mechanism or by another mechanism.
Balancing unit can be installed on the internal-combustion engine, and can be mechanically driven via the bent axle of motor.The Mechanical Driven of at least one balancing unit is that the example of the internal-combustion engine of haulage gear is favourable.
In internal-combustion engine, band drives or chain drives and is generally used for driving secondary assembly etc., and this band drives or chain drives and is commonly referred to haulage gear (and by this way name within the scope of the invention), wherein, is with or chain represents traction gear.
Haulage gear is intended to be used for transmitting large torque by redrawing (re-tensioning) with minimum possible energy loss and as far as possible little Cost of repair and maintenance.In this case, the drive unit of a plurality of secondary assemblies is bonded in the haulage gear usually.In order under tension force, to keep traction gear and therefore to guarantee the as far as possible driving of safety and gearless, guiding traction gear and in the appropriate location that transversely its tension device that applies power is arranged on usually drive unit with respect to direction of pull, the result is that drive unit is in tension state continuously.
The bond quality balance the particularly important is and guarantees fricton-tight driving, and this is because counterweight does not position in the expectation mode with respect to bent axle.In this respect, the chain as traction gear has advantage than sliding zone.
For this reason, the example of internal-combustion engine also can be advantageously, and wherein, the Mechanical Driven of at least one balancing unit is the gear drive of guaranteeing without the slippage driving.
Interrupted unit comprises that the example of the internal-combustion engine of clutch is favourable.
By clutch, particularly by opening clutch, the force flux between interrupt machine driven equilibrium unit and the mechanical actuation device reliably.
If at least one balancing unit is included in the axle of an one free end configuration driven gear, then friction clutch can be arranged between actuation gear and this axle or be arranged on actuation gear and be configured between the counterweight on this axle.
When using gear drive, can interrupt force flux by separating a gear, the result is that gear no longer is engaged with each other under the closed condition of balancing unit.
The example that has the internal-combustion engine of at least two parts that can be rotated toward each other around running shaft as nonequilibrium at least one counterweight is favourable.
This example is especially favourable about the opening process of at least one balancing unit, during at least one balancing unit opening process, balancing unit and crank-driven synchronously and the rotational speed of bent axle and counterweight adapt to each other or mate.Under specific circumstances, counterweight has to accelerate from state of rest.Because counterweight is not rotated with crankshaft-synchronous during accelerating process, so if counterweight as its whole effects of non-equilibrium generation, then is disadvantageous.For this reason, two parts that form counterweight are preferably orientated 180 ° of mutual skews as when the beginning opening process, and the result is that these two parts are externally eliminated on the effect each other, for example cancels each other out.By rotating in two parts, at first generate non-equilibrium and form as nonequilibrium at least one counterweight.In the working position, preferably, two parts no longer have any side-play amount, and this partial rotation is 180 ° for this reason.
It is favourable being provided for making during opening process the example of the internal-combustion engine of the synchronous device of at least one balancing unit and crank-driven.
In order to produce mass balance, at least one counterweight of the balancing unit that its counterweight is rotated as uneven part and around running shaft can have specific, constant precalculated position with respect to bent axle (for example, about crank-driven).On this degree, balancing unit can be synchronous with crank-driven in the scope of opening process.
The example of the internal-combustion engine of the device that in this case, is provided for locating (for example, limit stoper and/or locking device) is favourable.
In being equipped with the internal-combustion engine of engine controller, switch by engine controller and/or the example of the internal-combustion engine that the synchronous fact limits is favourable by at least one balancing unit.
The example that three cylinders arrange internal-combustion engine in a row is favourable.The advantage of in-line arrangement three cylinder engines is, can come balance one order inertia power and second-order inertia power by selecting suitable crankshaft crank and suitable ignition order.
For this reason, also be favourable by selecting suitable crankshaft crank and suitable ignition order to come the example of in-line arrangement three cylinder IC engines of balance one order inertia power and second-order inertia power.
Can compensate the moment that is caused by one order inertia power by single trunnion shaft, wherein, single trunnion shaft provides two counterweights that are configured and are used as non-equilibrium (unbalance) with 180 ° skew with the engine speed rotation and at its place, end on the direction opposite with bent axle.
Therefore, the example of in-line arrangement three cylinder engine also is favourable, wherein, at least one balancing unit comprises at least two counterweights, at least two counterweights are configured to be spaced apart from each other at axle, the moment of inertia that is positioned to be offset 180 ° and is equilibrated at effective generation in the central plane that extends by built-in cylinder.
In this case, the example of internal-combustion engine is favourable, and wherein, the counterweight with deviation post has the distance identical with the central plane of internal-combustion engine and has same large quality.
As mentioned above, balancing unit can be arranged on the internal-combustion engine of installing in the vehicle.Fig. 3 is the exemplary description of vehicle 100.Vehicle 100 comprises wheel 102.Moment of torsion offers wheel 102 via motor 10 and speed changer 104.In some instances, motor and fluid pressure motor also can offer moment of torsion wheel 102.Alternator 110 can be connected to motor 10 via axle or pulley machinery.Battery 108 and alternator 110 can offer electric energy unshowned various engine accessory parts among Fig. 3.
In Fig. 3 controller 12 is shown traditional microcomputer, it comprises microprocessor unit, input/output end port, ROM (read-only memory), random access memory, keep-alive storage and traditional data bus.Controller 12 is shown receives various signals from the sensor that is connected to motor 10, comprise coming the engine position signals of the hall effect sensor 20 of self-inductance measurement crank position.In aspect this explanation preferred, engine position sensor generates the equally spaced pulse of predetermined quantity when the rotating each time of bent axle, therefrom can determine engine speed (RPM).The All aspects of that controller 12 controls comprise the vehicle 100 of motor 10 and balancing unit 16 also are shown.In some instances, controller 12 can be controlled the position of the counterweight of balancing unit.
Fig. 4 is the flow chart that illustrates be used to the method 150 of utilizing balancing unit balanced engine of the present invention.Function as at least one operating parameter of internal-combustion engine switches at least one balancing unit.
In step 152, method 150 comprises determines that whether engine speed is greater than threshold value, such as 1000RPM.At low rotational speed place, the inertial force of motor can cause noise and vibration to disturb, and therefore, can enable balancing unit and disturb to offset.At the higher rotational place, because the fuel economy problem of the frictional loss meeting of balancing unit experience motor, therefore, the balancing unit of can stopping using at the speed place that is higher than threshold value.
Therefore, if the speed of motor is not higher than threshold value, then method proceeds to step 154, to enable balancing unit by the axle of spin balancing unit.As mentioned above, can the Mechanical Driven axle, and balancing unit can comprise the first quality and the second quality.In addition, at step 156 place, the first quality of balancing unit and the second quality can keep 180 ° at interval, until the speed of this axle equals the speed of bent axle.In case speed equates, at step 158 place, with respect to the first Mass movement the second quality so that quality aim at.
The description of carrying out according to internal-combustion engine of the present invention described above also is applied to the method according to this invention.
According to the present invention, switch balancing unit as the function of at least one operating parameter of internal-combustion engine.In the situation that in-line arrangement three cylinder engine, for example, the method according to this invention is at low rotational speed place and allow mass balance in idling mode, and for relatively high rotational speed, for loss and the corresponding fuel consumption of reducing friction, disconnect balancing unit and need not mass balance.
The example that switches the method for at least one balancing unit as the function of the rotational speed n of internal-combustion engine is favourable.According to the method modified example, the rotational speed n of internal-combustion engine is as at least one operating parameter of opening and disconnecting the function of balancing unit.Because moment of inertia and inertial force are rotated with engine speed or many times of engine speeds and carry out relevant mass balance by corresponding rotation counterweight, so mass balance has substantial connection owing to the principle that relates to engine speed, for this reason, the rotational speed n of internal-combustion engine also is for implementing balancing unit or the open loop control of interrupted unit and/or the proper handling parameter of closed loop control.
As long as the rotational speed n of internal-combustion engine surpasses predetermined rotational speed n
Threshold, upThe method example that just disconnects at least one balancing unit (supposing the balancing unit of running) is favourable.
Above method modified example allow by the balancing unit of opening or enable in the in-line arrangement three cylinder engine, be equilibrated at low rotational speed place and in idling mode by the caused moment of one order inertia power, and for the balancing unit of stopping using of high rotation speed relatively, wherein, when surpassing predetermined rotational speed n
Threshold, upThe time, do not require immediately balancing unit.
The certain benefits of the modified example of discussing is the higher rotational place disconnection balancing unit that is generally maximum value (for example, in the performance plot zone of internal-combustion engine) in frictional loss, wherein, obviously can save fuel oil by disconnecting balancing unit.
In this case, as long as the rotational speed of internal-combustion engine surpasses predetermined rotational speed n
Threshold, upAnd predetermined time cycle Δ t
1Interior greater than this predetermined rotational speed n
Threshold, up, the method example that just disconnects at least one balancing unit is favourable.
Introducing the supplementary condition that are used at least one balancing unit of disconnection is intended to prevent only temporarily surpass predetermined rotational speed in rotational speed, and then descend or surpass being used near the fluctuation predetermined value of rotational speed in the situation that proof disconnects balancing unit and switching too continually the balancing unit of especially stopping using.
For above-mentioned reason, the method modified example also is advantageously, wherein, as long as the rotational speed n of internal-combustion engine is lower than predetermined rotational speed n
Threshold, down, just open at least one balancing unit (supposing the balancing unit of non-running).
In this case, as long as the rotational speed n of internal-combustion engine is lower than predetermined rotational speed n
Threshold, downAnd predetermined time cycle Δ t
2In be lower than this predetermined rotational speed n
Threshold, downThe method example of just opening at least one balancing unit also is favourable.
Surpass rotational speed n with reference to combination
Threshold, upWith time cycle Δ t
1The statement of carrying out.Use in a similar fashion about the statement that these method modified examples are carried out.
In the in-line arrangement three cylinder engine, for example, when being lower than predetermined rotational speed n
Threshold, downThe time, for balance by the moment that one order inertia power produces, it is favourable enabling balancing unit.
Except being defined for the specific rotational speed n that disconnects and open balancing unit
Threshold, upOr n
Threshold, downOutside, the rotational velocity range that can also limit balancing unit work or keep stopping using.
Have can be in the internal-combustion engine of at least two parts that running shaft rotates relative to one another as nonequilibrium at least one counterweight, the method example can be favourable, wherein, be positioned as the balancing unit of the non-running of Rotate 180 relative to each other ° by hypothesis, during the opening process of balancing unit, in the first method step, balancing unit is accelerated and is synchronous with crank-driven, and in the second method step, form as nonequilibrium counterweight by at least two parts of rotation.
Therefore, method and system shown in above provides engine method, comprise: under first condition, running shaft is with the spin balancing unit, this balancing unit is included in the first quality and the second quality that is configured to 180 ° at interval on the axle, and as long as the speed of axle equals the speed of engine crankshaft, just with respect to the first Mass movement the second quality, until the first quality and the second quality are aimed at axle.
The method also comprises: under second condition, declutch shaft is to stop the rotation of axle.First condition can comprise that engine speed is lower than first threshold, and second condition can comprise that engine speed is higher than threshold value.Declutch shaft may further include via clutch release shaft.
Should be appreciated that structure disclosed herein and to be arranged in be exemplary in essence, and these specific embodiments should not understand in restrictive meaning, because numerous modification is possible.For example, top technology can be applicable to V-6, I-4, I-6, V-12, opposed 4 cylinders and other engine types.Theme of the present disclosure comprises all novel and non-obvious combination and sub-portfolios of various system disclosed herein and structure and other features, function and/or attribute.
Claims particularly point out and are considered to novel and apparent particular combinations and sub-portfolio.These claims may relate to " element " or " the first element " or be equal to appellation.Such claim is appreciated that the combination that comprises one or more this elements, both neither requiring nor excluding two or more this elements.Can be by to the modification of current claim or by in the application or related application, proposing other combinations and the sub-portfolio that new claim is come claimed disclosed feature, function, element and/or attribute.Require to compare wider on scope, narrower, identical or different from original rights, these claims also are construed to be included in the theme of the present disclosure.
Claims (20)
1. internal-combustion engine with at least one cylinder that is associated with crank driven mechanism comprises:
At least one the mechanically operated balancing unit that is used for balance inertial force, described balancing unit comprise that rotating first quality for the second quality around running shaft by initial phase when described balancing unit running is used as nonequilibrium at least one counterweight; And
Interrupted unit, it makes described at least one balancing unit and mechanical actuation device disconnect under off state and under opening state described at least one balancing unit is connected to described mechanical actuation device.
2. internal-combustion engine according to claim 1, wherein, the described mechanical actuation device of described at least one balancing unit is haulage gear.
3. internal-combustion engine according to claim 1, wherein, the described mechanical actuation device of described at least one balancing unit is gear device.
4. internal-combustion engine according to claim 1, wherein, described interrupted unit comprises clutch.
5. internal-combustion engine according to claim 1 wherein, has at least two parts that can rotate relative to one another around described running shaft as nonequilibrium described at least one counterweight.
6. internal-combustion engine according to claim 1, wherein, described at least one balancing unit is synchronous with described crank driven mechanism during opening process.
7. internal-combustion engine according to claim 6 further comprises be used to the locking framework of locating described at least one balancing unit and/or position-limit mechanism.
8. internal-combustion engine according to claim 1 wherein, further comprises engine controller, wherein, opens and disconnects described at least one balancing unit by described engine controller.
9. internal-combustion engine according to claim 1, wherein, described internal-combustion engine comprises three cylinders in a row is set.
10. internal-combustion engine according to claim 9 wherein, comes balance one order inertia power and second-order inertia power by selecting suitable crankshaft crank and suitable ignition order.
11. internal-combustion engine according to claim 9, wherein, described at least one balancing unit comprises two counterweights, and described two counterweights are configured to be spaced apart from each other at axle, are positioned to be offset 180 ° and be equilibrated at the moment of inertia that effectively generates in the central plane that extends by built-in cylinder.
12. internal-combustion engine according to claim 11 wherein, has the counterweight of deviation post and the central plane of built-in cylinder and has same distance and have onesize quality.
13. a method that is used for operating internal-combustion engines comprises:
Open and disconnect at least one mechanically operated balancing unit according at least one operating parameter of described internal-combustion engine, described at least one balancing unit comprises at least one counterweight, described at least one counterweight is used as non-equilibrium and rotates around running shaft when balancing unit turns round
Wherein, interrupted unit makes described at least one balancing unit and mechanical actuation device disconnect under off state and under opening state described at least one balancing unit is connected to described mechanical actuation device.
14. method according to claim 13 wherein, is opened and is disconnected described at least one balancing unit according to the rotational speed n of described internal-combustion engine.
15. method according to claim 13, wherein, have at least two parts that can rotate relative to one another around described running shaft as nonequilibrium described at least one counterweight, and described method further comprises: if the non-running of described balancing unit, wherein, various piece relative to each other Rotate 180 ° positions, then when described balancing unit is opened:
Accelerate described balancing unit and make described balancing unit and crank driven mechanism synchronous; And
Rotation is as described at least two parts of nonequilibrium counterweight.
16. the method for a motor comprises:
Under first condition,
Running shaft spin balancing unit, described balancing unit are included in the first quality and the second quality that is configured to 180 ° at interval on the described axle; And
In case the speed of described axle equals the speed of the bent axle of motor, just with respect to described the second quality of described the first Mass movement until described the first quality and described the second quality aim at described axle.
17. method according to claim 16 further comprises: under second condition, separate described axle to stop the rotation of described axle.
18. method according to claim 17, wherein, described first condition comprises that engine speed is lower than threshold value, and described second condition comprises that engine speed is higher than described threshold value.
19. method according to claim 17 wherein, is separated described axle and is further comprised via the described axle of clutch separation.
20. method according to claim 16, wherein, described shaft mechanical is connected to the described bent axle of described motor.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102011080602.4 | 2011-08-08 | ||
| DE102011080602.4A DE102011080602B4 (en) | 2011-08-08 | 2011-08-08 | Method for operating an internal combustion engine with mass balance |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102927198A true CN102927198A (en) | 2013-02-13 |
| CN102927198B CN102927198B (en) | 2016-04-27 |
Family
ID=47595460
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210279667.0A Expired - Fee Related CN102927198B (en) | 2011-08-08 | 2012-08-07 | There is the internal-combustion engine of mass balance and the method for operating this internal-combustion engine |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US9051991B2 (en) |
| CN (1) | CN102927198B (en) |
| DE (1) | DE102011080602B4 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103438147A (en) * | 2013-08-29 | 2013-12-11 | 长城汽车股份有限公司 | Engine balance shaft |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102011080601A1 (en) * | 2011-08-08 | 2013-02-14 | Ford Global Technologies, Llc | Method for balancing the inertial forces of an internal combustion engine and internal combustion engine for carrying out such a method |
| JP6365840B2 (en) * | 2014-12-22 | 2018-08-01 | 三菱自動車工業株式会社 | Balancer device for internal combustion engine |
| EP3211266B1 (en) * | 2016-02-18 | 2019-12-11 | Ford Global Technologies, LLC | An engine balance assembly using electric motors, and method of balancing vibrations |
| GB2556896B (en) | 2016-11-23 | 2019-02-20 | Ford Global Tech Llc | An engine assembly |
| KR101755496B1 (en) * | 2016-09-09 | 2017-07-10 | 현대자동차 주식회사 | Power train |
| CN109296455B (en) * | 2018-11-03 | 2022-08-30 | 肖光宇 | Piston reciprocating tank engine |
| CN114109591B (en) * | 2021-10-21 | 2023-01-24 | 神龙汽车有限公司 | Three-cylinder engine assembly unbalance debugging method |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4556026A (en) * | 1983-08-31 | 1985-12-03 | Mazda Motor Corporation | Multiple-displacement engine |
| CN1268631A (en) * | 1999-03-31 | 2000-10-04 | 本田技研工业株式会社 | Compensation of inertia forces device for vehicle engine |
| CN201330649Y (en) * | 2008-12-03 | 2009-10-21 | 济南轻骑发动机有限公司 | GS250 engine |
| US7617810B1 (en) * | 2007-12-03 | 2009-11-17 | Brunswick Corporation | Counterweight shaft construction which reduces lubricant aeration |
| CN101823420A (en) * | 2009-03-02 | 2010-09-08 | 朱心平 | Hybrid power system for automobile |
Family Cites Families (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5839843A (en) * | 1981-08-31 | 1983-03-08 | Fuji Heavy Ind Ltd | Balancer for three-cylinder engine |
| DE3312105A1 (en) | 1983-04-02 | 1984-10-04 | Volkswagenwerk Ag, 3180 Wolfsburg | Mass-balancing device |
| DE4211629B4 (en) | 1992-04-07 | 2004-11-11 | Bayerische Motoren Werke Ag | Mass force compensation and / or alternating torque compensation on reciprocating machines |
| JP3194568B2 (en) | 1995-07-31 | 2001-07-30 | ヤマハ発動機株式会社 | Chain drive mechanism of internal combustion engine |
| JPH10280973A (en) | 1997-04-08 | 1998-10-20 | Otix:Kk | Blancer mechanism for internal combustion engine, and its driving method |
| US7086366B1 (en) | 1999-04-20 | 2006-08-08 | Metaldyne Machining And Assembly Company, Inc. | Energy efficient fluid pump |
| US6581495B2 (en) * | 2000-01-26 | 2003-06-24 | International Engine Intellectual Property Company, Llc | Balancer shaft |
| JP4390580B2 (en) | 2004-02-12 | 2009-12-24 | 株式会社オティックス | Balancer mechanism |
| JP2008014351A (en) * | 2006-07-04 | 2008-01-24 | Hitachi Ltd | Engine balancer device |
| EP1923600B1 (en) | 2006-11-20 | 2018-09-19 | Ford Global Technologies, LLC | Counterweight system for an internal combustion engine in a motor vehicle |
| DE102007053604B4 (en) | 2007-11-10 | 2013-01-10 | Audi Ag | Internal combustion engine with speed-dependent balance shaft coupling |
| DE102008012682A1 (en) | 2008-03-05 | 2009-09-10 | Audi Ag | Clutch for connecting balancing shaft with crankshaft of internal-combustion engine, has annular gear that is mounted on crankshaft, and is connected with crankshaft by switching mechanics in force-fit manner |
| JP5206069B2 (en) | 2008-03-28 | 2013-06-12 | 株式会社豊田自動織機 | Inline 3-cylinder engine balancer mechanism |
| DE102008021682A1 (en) | 2008-04-30 | 2009-11-05 | Magna Powertrain Ag & Co Kg | Method for assembling a structural unit |
| FR2948159A1 (en) | 2009-07-17 | 2011-01-21 | Renault Sa | Internal combustion engine for use in motor vehicle, has coupling unit provided with disengaging unit and setting unit, and setting unit that sets angular position of balancing device around balancing axis with respect to driving axis |
| DE102009047545A1 (en) | 2009-12-04 | 2011-06-09 | Ford Global Technologies, LLC, Dearborn | Multi-cylinder in-line internal combustion engine e.g. three-cylinder engine, for motor vehicle, has balancing masses that are arranged such that balancing of inertia forces corresponds to specific percent balancing of mass forces |
| DE102011000585A1 (en) | 2011-02-09 | 2012-08-09 | Ford Global Technologies, Llc. | Multi-cylinder in-line internal combustion engine for a motor vehicle, and method for operating the same |
-
2011
- 2011-08-08 DE DE102011080602.4A patent/DE102011080602B4/en not_active Expired - Fee Related
-
2012
- 2012-07-26 US US13/559,498 patent/US9051991B2/en not_active Expired - Fee Related
- 2012-08-07 CN CN201210279667.0A patent/CN102927198B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4556026A (en) * | 1983-08-31 | 1985-12-03 | Mazda Motor Corporation | Multiple-displacement engine |
| CN1268631A (en) * | 1999-03-31 | 2000-10-04 | 本田技研工业株式会社 | Compensation of inertia forces device for vehicle engine |
| US7617810B1 (en) * | 2007-12-03 | 2009-11-17 | Brunswick Corporation | Counterweight shaft construction which reduces lubricant aeration |
| CN201330649Y (en) * | 2008-12-03 | 2009-10-21 | 济南轻骑发动机有限公司 | GS250 engine |
| CN101823420A (en) * | 2009-03-02 | 2010-09-08 | 朱心平 | Hybrid power system for automobile |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103438147A (en) * | 2013-08-29 | 2013-12-11 | 长城汽车股份有限公司 | Engine balance shaft |
| CN103438147B (en) * | 2013-08-29 | 2015-10-28 | 长城汽车股份有限公司 | Balance shaft of engine |
Also Published As
| Publication number | Publication date |
|---|---|
| US20130036996A1 (en) | 2013-02-14 |
| CN102927198B (en) | 2016-04-27 |
| DE102011080602A1 (en) | 2013-02-14 |
| US9051991B2 (en) | 2015-06-09 |
| DE102011080602B4 (en) | 2018-03-01 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102927198B (en) | There is the internal-combustion engine of mass balance and the method for operating this internal-combustion engine | |
| US9121472B2 (en) | Internal combustion engine with compensation weight arranged on the crankshaft and serving as an imbalance, and method for production of the crankshaft | |
| US7178497B2 (en) | Inertial torque reaction management with selectively engageable counter rotating component | |
| RU152079U1 (en) | INTERNAL COMBUSTION ENGINE WITH PENDULUM DEVICE | |
| US20150285333A1 (en) | Production feasible pendulum crankshaft | |
| Newland | Developments in the Design of Centrifugal Pendulum Vibration Absorbers. | |
| CA2574852A1 (en) | Traction drive | |
| CN115450771A (en) | Skip-to-stop mode for avoiding engine resonance | |
| KR20070026527A (en) | Belt drive for an internal combustion engine | |
| US20140311441A1 (en) | Internal combustion engine with compensation weight arranged on the crankshaft and serving as an imbalance, and method for production of the crankshaft | |
| RU2666480C2 (en) | Pendulum crankshaft for internal combustion engine | |
| EP3327310B1 (en) | An internal combustion engine assembly with engine balancing shafts using electric motors | |
| CN102927199A (en) | A method for balancing inertia forces of an internal combustion engine and the internal combustion engine carrying out such method | |
| US20130167793A1 (en) | Method to balance mass moments of a drive unit and drive unit for performance of such a method | |
| US6655340B2 (en) | Engine with balancer for second order pitching couple | |
| GB2547509B (en) | An engine balance assembly using electric motors to adjust phase angle or rotational speed of the motors' shafts | |
| CZ297752B6 (en) | Multifunctional balancing system | |
| KR20140004843A (en) | Apparatus for damping of flywheel | |
| KR101219335B1 (en) | Multi mode type torsion damper system | |
| EP3578777B1 (en) | Accessory mounting structure for engine | |
| JP2007046633A (en) | Balancer device of engine | |
| KR100435960B1 (en) | Balance shaft having magnetic clutch | |
| EP3211266B1 (en) | An engine balance assembly using electric motors, and method of balancing vibrations | |
| JP2015224685A (en) | Vibration suppressing mechanism of engine | |
| EP3867119A1 (en) | A hybrid drive module, and a method for improving performance of such hybrid drive module |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20160427 Termination date: 20210807 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |